CN103261590B - The telescoping valve sealing improved - Google Patents

The telescoping valve sealing improved Download PDF

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Publication number
CN103261590B
CN103261590B CN201180059309.2A CN201180059309A CN103261590B CN 103261590 B CN103261590 B CN 103261590B CN 201180059309 A CN201180059309 A CN 201180059309A CN 103261590 B CN103261590 B CN 103261590B
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China
Prior art keywords
valve
sealing
margin
telescoping
valve seat
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CN201180059309.2A
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CN103261590A (en
Inventor
詹姆斯·M·克利维斯
迈克尔·霍克斯
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Pinnacle Engines Inc
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Pinnacle Engines Inc
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L5/00—Slide valve-gear or valve-arrangements
    • F01L5/04—Slide valve-gear or valve-arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • F01L5/06—Slide valve-gear or valve-arrangements with cylindrical, sleeve, or part-annularly shaped valves surrounding working cylinder or piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B7/00—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F01B7/02—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with oppositely reciprocating pistons
    • F01B7/04—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with oppositely reciprocating pistons acting on same main shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
    • F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
    • F02B25/04—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke
    • F02B25/06—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke the cylinder-head ports being controlled by working pistons, e.g. by sleeve-shaped extensions thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
    • F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
    • F02B25/08—Engines with oppositely-moving reciprocating working pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F02B75/282—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders the pistons having equal strokes

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

There is the telescoping valve of valve body, valve body at least in part around at least one with the piston of reciprocating manner movement, telescoping valve and at least one piston can define the firing chamber of internal-combustion engine at least in part.Valve brake structure can flow through engine port with control by moving sleeve valve between open and closed positions.When telescoping valve is moved to closed position, the sealing the margin of telescoping valve is pushed by the Driving force produced by valve actuating structure and props up valve seat.At least one in telescoping valve and valve seat comprises valve supplemental characteristic.This supplemental characteristic helps valve brake structure to resist the power contrary with Driving force produced by internal-combustion engine.Related product, system and method will be described.

Description

The telescoping valve sealing improved
quoting alternately related application
The application requires according to 35U.S.C. § 119 (e) the U.S. Provisional Application case 61/391,519 that on October 8th, 2010 submits, and patent name is the preference of " ImprovedInternalCombustionEngineValveSealing ".The application relates to total U. S. Patent 7,559,298, total and co-pending name is called the International Application Serial No. PCT/US2011/055457 of " SinglePistonSleeveValvewithOptionalVariableCompressionRa tioCapability ", and total and co-pending name is called international application and total and co-pending name is called the International Application Serial No. PCT/US2011/055485 of " PositiveControl (Desmodromic) ValveSystemsforInternalCombustionEngines ".Each application listed by this section or the disclosure of patent and accompanying drawing are to be incorporated in this with reference to mode.
Technical field
The disclosure relates generally to field of internal combustion engine, in certain embodiments, relates to the valve system used with telescoping valve.
Background technique
Telescoping valve is a kind of valve that can use in internal-combustion engine, internal-combustion engine includes but not limited to opposed piston type engine, in opposed piston type engine, two pistons share a single cylinder, telescoping valve is also a kind of valve used within the engine, and each piston is reciprocating in its oneself cylinder within the engine.This valve forms part or all of cylinder wall usually.In some changes, one or more telescoping valve can be roughly parallel to an axle and move back and forth, one or more pistons on this axle move back and forth, to open and close suction port and/or relief opening at reasonable time thus to introduce air or air-fuel mixture enters firing chamber, and/or discharge products of combustion from firing chamber.In other changes, one or more telescoping valve can to rotate and/or along the axle translation of piston around the axle of piston, with one that opens and closes in suction port and relief opening or will both open and close.Due to the potential big circumference open area that can be controlled by telescoping valve, such valve can provide a larger cross sectional area for flowing at the fluid of open position.
Summary of the invention
According to the All aspects of of current theme, system can comprise one or more valve supplemental characteristic, such as, Interference angle such as between telescoping valve and valve seat is configured to make the telescoping valve produced by combustion-gas pressure bend the gap can not opened between telescoping valve sealing the margin and valve seat, this gap is that combustion-gas pressure exposes enough large surface area to act on applying counter-force, and this counter-force is enough to overcome the mechanical force keeping telescoping valve to close.Also possible within the scope of current theme is method for the design of regulating sleeve valve system and the attribute of Design and manufacture, method considers the comparatively macrobending power of the low compression engine operation of variable compression ratio engine, and attribute can guarantee favourable telescoping valve geometrical shape and its corresponding valve seat can be maintained in the working life of much of its.
In one aspect, system comprises telescoping valve, and this telescoping valve comprises valve body, this valve body at least in part around at least one with the piston of reciprocating manner movement.Telescoping valve and at least one piston define the firing chamber of internal-combustion engine at least in part.Valve actuating structure between open and closed positions moving sleeve valve flows through a port of internal-combustion engine with control.When telescoping valve moves to closed position, the sealing the margin of telescoping valve is propped up valve seal by the Driving force produced by valve actuating structure.At least one in telescoping valve and valve seat comprises valve miscellaneous function, and this function Auxiliary valves actuating structure resists the power contrary with Driving force produced by internal-combustion engine.The power contrary with Driving force produced by internal-combustion engine is included in the pressure of the combustion gas in firing chamber, and this pressure acts on the surface of the exposure of sealing the margin on the direction contrary with the valve closing force of valve actuating structure.
One be associated in, method comprise by valve actuating structure between open and closed positions moving sleeve valve to control to flow through a port of internal-combustion engine.Casing valve comprises valve body, this valve body at least in part around at least one with the piston of reciprocating manner movement.Telescoping valve and at least one piston define the firing chamber of internal-combustion engine at least in part.When telescoping valve moves to closed position, the sealing the margin of telescoping valve is propped up valve seat by the Driving force produced by valve actuating structure.Valve miscellaneous function Auxiliary valves actuating structure resists the power contrary with Driving force produced by internal-combustion engine.At least one in telescoping valve and valve seat comprises valve miscellaneous function or function.The power contrary with Driving force produced by internal-combustion engine is included in the pressure of the combustion gas in firing chamber, and this pressure acts on the surface of the exposure of sealing the margin on the direction contrary with the valve closing force of valve actuating structure.
In some changes, one or more in following functions are optionally included in any feasible combination.Valve actuating structure comprises spring alternatively, and the size of this spring is suitable for guaranteeing that maximum gas pressure can not depart from valve seat in lift-off seal edge.Valve miscellaneous function comprises the Interference angle between the sealing the margin of valve and valve seat alternatively, when telescoping valve is bent outwardly due to the radial force caused by the pressure of the combustion gas in firing chamber, Interference angle is configured to formed by the clearance opening reduced between sealing the margin and valve seat thus reduced the surface area exposed.Interference angle comprises the difference between the first cone angle of sealing the margin and the second cone angle of valve seat alternatively.Interference angle is formed between the first sealing surfaces on sealing the margin and the second sealing surfaces on valve seat alternatively.First sealing surfaces is formed the shape of first portion of picture the first rotating tip solid alternatively, the first rotating tip solid have the first sealing surfaces towards the first summit.Second sealing surfaces is formed the shape of second portion of picture the second rotating tip solid alternatively, the second rotating tip solid have the second sealing surfaces towards the second summit.Their running shaft and the central shaft of firing chamber are shared by each alternatively for first rotating tip solid and the second rotating tip solid.
The second rotating tip solid that first rotating tip solid comprises the first cone and rotation alternatively comprises the second cone alternatively.First summit and the second summit are alternatively all towards closed position, or the first summit and the second summit are alternatively all towards open position.
Tilt or sharp-pointed Interference angle can be formed between the first sealing surfaces and the second sealing surfaces.Due to the pressure maximum of the combustion gas in firing chamber, Interference angle alternatively by based on telescoping valve by the maximum deflection estimated.Interference angle causes the inner edge of sealing the margin to keep contacting with valve seat, even when maximum deflection alternatively.
Internal-combustion engine comprises opposed piston type engine alternatively.In the optional change of opposed piston type engine, at least one piston comprise alternatively at least in part by valve body circumvents first piston and at least in part by the second telescoping valve the second valve body circumvents at back piston.Can the to-and-fro motion between respective top dead center and bottom dead center position of inharmonic mode at first piston and the second piston, thus make before arriving device top dead center position at back piston, first to arrive its top dead center position to provide variable compression ratio performance at first piston.Second telescoping valve comprises the second sealing the margin of propping up the second valve seat and the second Interference angle being greater than Interference angle between second sealing the margin and the second valve seat of the second telescoping valve alternatively.
In the second optional change of opposed piston type engine, at least one piston comprises alternatively at least in part by the main piston of valve body circumvents with at least in part by the secondary piston of the second valve body circumvents of the second telescoping valve.Main piston and secondary piston can respective top dead centers on the first and second respective arbors and moving back and forth between lower dead center.Second arbor along the axis of movement translation of secondary piston, thus can make to have top dead center position compared with the secondary piston in low compression ratio configuration, and the distance of this position distance engine center is distal to the distance apart from main piston.Second telescoping valve comprises the second sealing the margin of propping up the second valve seat and the second Interference angle being greater than Interference angle between second sealing the margin and the second valve seat of the second telescoping valve alternatively.
Sealing the margin comprises multiple angle alternatively.Multiple angle comprises first jiao alternatively, this angle soften or cut sealing the margin other sharp changes to eliminate heating too fast of sealing the margin; Comprise the angle of the second coupling valve seat of Interference angle alternatively; And the 3rd, relax angle, this angle is more precipitous than the wrapping angle of telescoping valve and valve seat substantially, thus when telescoping valve and the prooving of valve seat, telescoping valve can not bend to such an extent as to sealing the margin contacts with valve seat and the 3rd, relief areas.
The details of the one or more change of the present invention is set forth in following appended accompanying drawing and specification.By specification, drawings and the claims, other features and advantages of the present invention described herein will be apparent.
Accompanying drawing explanation
Accompanying drawing, as a part for specification, reflects some aspect of the present invention, helps to understand the principle be associated with specific embodiment together with specification.In the accompanying drawings:
Fig. 1 illustrates the sectional drawing of part internal-combustion engine, wherein two opposed pistons to-and-fro motion in cylinder;
Fig. 2 shows the cross-sectional view of the part internal-combustion engine shown in Fig. 1;
Fig. 3 illustrates the cross-sectional view of part internal-combustion engine, and wherein at least one in each cylinder in to-and-fro motion and suction port and relief opening of single piston is opened and closed by telescoping valve;
Fig. 4 A, 4B, 4C, 4D, 4E and 4F illustrate the cross-sectional view of the bending effect that telescoping valve sealing is described;
Fig. 5 A, 5B, 5C and 5D illustrate the cross-sectional view illustrating and strengthen seal sleeve valve feature;
Fig. 6 A, 6B, 6C and 6D illustrate the cross-sectional view illustrating and strengthen seal sleeve valve feature;
Fig. 7 A, 7B and 7C illustrate cross-sectional view and sectional drawing that double-walled gas auxiliary socket valve feature is described;
Fig. 8 illustrates the cross-sectional view that double-walled gas auxiliary socket valve feature is described;
Fig. 9 A, 9B, 9C and 9D illustrate illustrate telescoping valve air-circulation features etc. axle figure;
Figure 10 illustrates the sectional drawing that telescoping valve feature is described;
Figure 11 A, 11B, 11C illustrate the feature that telescoping valve encapsulating method is described etc. axle and cross-sectional view; And
Figure 12 illustrates to set forth to have the flow chart realizing each side of the method for consistent feature one or more and of the present invention.
When feasible, similar reference number represents similar structure, function or element.
Embodiment
Fig. 1 shows the part sectioned view of the internal-combustion engine 100 with a pair opposed pistons, and it comprises first piston 102 and the second piston 104.First piston 102 is operationally coupled to the first arbor 106 by first connecting rod 110, and the second piston 104 is by second connecting rod 114, to be operationally coupled to the second arbor 112.As shown in Figure 1, the first arbor 106 is operationally coupled to the second arbor 112 by the gear of motion that is synchronously a series of or that otherwise control first piston 102 and the second piston 104.During power operation, first piston 102 and the second piston 104 in the cylindrical hole of the arranged in co-axial alignment formed by corresponding telescoping valve towards with to-and-fro motion away from each other.More specifically, first piston 102 is front-rear reciprocation movement in exhaust sleeve valve 116, and the second piston 104 front-rear reciprocation movement in corresponding air inlet telescoping valve 120.Exhaust sleeve valve 116 and air inlet telescoping valve 120 also can open and close corresponding relief opening 122 and suction port 124 with the reasonable time in engine cycles by front-rear reciprocation movement respectively, thus transmission air and/or fuel are to firing chamber 126, it defined by exhaust and air inlet telescoping valve 116,120 and first and second piston 102,104 at least in part.
Fig. 2 illustrates cross section Figure 200 of the internal-combustion engine 100 of Fig. 1.As the further elaboration in Fig. 2, the first pivot rocking arm 230 (being also referred to as " rocking bar " 230) has and operates the proximal part contacted and the distal portions being operationally coupled to exhaust sleeve valve 116 with the first corresponding nose of cam 232.First pivot rocking arm 230 opens exhaust sleeve valve 116, such as by the sealing the margin of mobile exhaust sleeve valve 116 away from its corresponding first valve seat 234.Similarly, pivot rocking arm 236 (being also referred to as " rocking bar " 240) has and operates the proximal part contacted and the distal portions being operationally coupled to air inlet telescoping valve 120 with the second nose of cam 240.Pivot rocking arm 236 opens air inlet telescoping valve 120, such as, by moving forward into the sealing the margin of gas telescoping valve 120 away from its corresponding second valve seat 242.
First nose of cam 232 is configurable on the first suitable camshaft, and it can operationally be coupled to corresponding arbor by one or more gear.At exhaust side, such as, the rotation of the first nose of cam 232 can in a direction (such as, drive from left to right) proximal part of the first rocking bar 230, this causes the distal portions of the first rocking arm 230 in contrary direction (such as conversely, from right to left) drive exhaust sleeve valve 116, thus open relief opening 122.Similar action can occur in air inlet side, wherein the rotation of the second nose of cam 240 can in a direction (such as, drive from right to left) proximal part of the second rocking arm 236, this causes again the distal portions of the second rocking arm 236 in the opposite direction (such as conversely, from left to right) drive air inlet telescoping valve 120, thus open suction port 124.
Each exhaust sleeve valve 116 and air inlet telescoping valve 120 are pressed onto operating position by by corresponding biasing element, biasing element is first helical spring 244 and second largest helical spring 246 such as, is wherein compressed between each flange on the bottom of corresponding telescoping valve and the counter surface being fixed to corresponding arbor.Under the control of the first nose of cam 232, first biasing element 244 orders about exhaust sleeve valve 116 from left to right to close relief opening 122, and under the control of the second nose of cam 240, the second biasing element 246 orders about air inlet telescoping valve 120 from right to left to close suction port 124.
In the process of operation motor 100, gas pressure directly acts at least part of exhaust sleeve valve 116 and the annular sealing edge of air inlet telescoping valve 120, and the piston side load to be produced by the piston rod angle relative to cylinder axis, can be tending towards tilting or otherwise respectively elevates exhaust gas telescoping valve 116 and air inlet telescoping valve 120 to depart from their respective first valve seat 234 and second valve seats 242.If exhaust sleeve valve 116 and air inlet telescoping valve 120 seal insufficient, some adverse consequencess may be caused, comprise burn valve, power loss, fuel economy are poor, accelerated wear test etc.
Fig. 3 shows an example of the motor 300 in non-opposed pistons configuration, and the first port 304 that this motor still uses telescoping valve 302 to open and close, this port can be relief opening or suction port.Poppet valve assembly 306 can control the opening and closing of the second port 310, this second port can be can't help telescoping valve 302 control other relief opening or suction port.Single telescoping valve 302 can control in the mode of similar above-mentioned control opposed piston type engine.In addition, equally within the scope of the present invention be non-opposed piston type engine, it comprises two telescoping valve, as such as CO-PENDING and the international patent application owned together be those telescoping valves described in PCT/US2011/055457.
Such telescoping valve, the linear reciprocating motion that what it mainly experienced is along reciprocating piston axis, can comprise sealing the margin usually, and sealing edge is forced into contact with valve seat and seals to be formed.In some instances, sealing the margin and valve seat can have the coniform angled surface of coupling, and this surface is designed to carry out overlap and pairing when sealing the margin and valve seat contact.But at high pressure, system must be suitably designed for penetrating the tendency offset and leak.In poppet valve internal-combustion engine firing chamber in air pressure trend towards acting on valve head to force the tapered circumference of valve head to valve seat to assist sealing, be different from poppet valve, telescoping valve is subject to the power to extrapolation, and away from valve seat instead of increase the power that produced by valve actuation system to force sealing the margin to valve seat.In other words, air pressure acts directly on one end of telescoping valve, and by the side load of piston in addition on valve, due to atmospheric pressure on piston and can be oblique in conjunction with departing from valve seat with the sealing the margin of inclined valve relative to the bar angle of cylinder-bore axis.In some motors, substantially can be used for overcoming this trend and maintaining valve edge props up valve seat along the spring of cylinder centerline.This lever arm resists the tilting moment caused by bar angle can be increased usually as improving the function of cylinder bore.But upset force itself generally determines size according to the area of piston (i.e. piston diameter square).Therefore, larger hole motor may need larger spring to cause a lower free frequency, and this frequency can be motor restriction speed operating range.
Method in the past for this problem uses hydraulic system to provide extra power to prop up valve seat safely to keep valve.Without the need to hydraulic system with actuated valve, keep seal mechanism as independently feature implementation cost may be very high.The U.S. Patent number 7,559 owned together, in another example described in 298, the tip part of the valve seat end of telescoping valve can be considered to help to keep sleeve to paste valve seat with air pressure.But, at the sealing the margin place of telescoping valve and/or use special shape can increase the complexity of design on valve seat, thus increase the manufacture cost of motor.
There is several factor to relate to and guarantee seal sleeve valve rightly.The air pressure being exposed to firing chamber acted on valve top surface may become to be attempted to promote the large power of of valve opening.The dislocation of hole and valve seat also may leak occur before limit maximum pressure.The diameter of the rigidity of valve material and thickness and valve also can affect sealability.The minimizing of pressure maximum before the sharp edge at destructive valve tip also may cause leaking.
Although valve and valve seat are very usual with slightly different angle contact ground in the example of poppet valve, in the example of telescoping valve, the method can be slightly different.In the example of telescoping valve, cause valve to promote the power departing from valve seat and leakage generally must be kept the structure that valve props up valve seat and carry out reaction.
Cause the bending of sleeve due to the air pressure in firing chamber, need the power keeping valve to prop up air pressure can be determined by the width of the width of the marginal gap on valve end in conjunction with the extra exposed area of valve end.If the hole that sleeve slides offsets relative to valve seat, need extra power to make colleting deformation with applicable valve seat wherein.In addition, piston side is carried and is tended to make sleeve tilt to lift off a seat.All these power needs to overcome in the structure keeping valve to prop up valve seat.
In order to solve these and the other problems that may occur with solution available at present, the method that one or more embodiment of the present invention provides, system, to manufacture a product etc. and may improve the sealability of internal-combustion engine middle sleeve valve.
A kind of method of the challenge of above-mentioned solution valve seal uses spring to prop up valve seat to force valve.The size of this spring can make it be equipped with enough strength at close stance and resist power listed above.But required maintenance valve closing and the power of sealing can be greater than required maintenance cam generation motion significantly and be in the lower required power of control.As an example, for the marginal gap of the holes of 51 millimeters and 0.25 millimeter, required spring force is the power of at least several times, and this power generally can be designed to the running speed of traditional limited production motor (6000 turns per minute) control valve action.Can higher than the Interference angle existed with the spring force required for the sealing of mating angle if obtained.Optimum interference angle can be characterized as being not mating between the taper of the sealing the margin of telescoping valve 402 and the taper of valve seat 404, this interference angle can be determined by several factor, these factors include but not limited to: the room compared to piston top ring position is pressed, the width of the marginal gap of the sealing the margin of valve, the angle of the modulus of the thickness of telescoping valve self, the modulus of telescoping valve material, seat material, telescoping valve diameter, valve seat, etc.
When Fig. 4 A and 4B series illustrate that engine system 400 middle sleeve valve 402 contacts with valve seat 404, its sealing difficulty that may run in deflection in radial directions.In Figure 4 A, the telescoping valve ground connection cone seal edge of telescoping valve 402 contacts with valve seat 404, and valve seat 404 not mate from the slightly different angle of sealing the margin and earth surface to make the taper at valve seal edge and valve seat 404 under air pressure approx.Therefore, a little gap 406 is positioned on the outside of telescoping valve 402, and this gap is exposed to port volume 410.In compression stroke and the expansion stroke subsequently after being included in the ignition mixture in firing chamber 126 and lighting a fire, along with piston 412 shifts to valve seat 404, the pressure of ignition mixture may cause telescoping valve 402 to be bent outwardly in the mode of the exaggeration shown in Fig. 4 B on piston top ring 414, and this figure is not pro rata.Telescoping valve 402 bending may cause gap 406 existing on the inner side of telescoping valve 402 to make experience on the surface of telescoping valve sealing the margin act on the high pressure of the firing chamber 126 on the contrary direction of the power contacted with valve seat 404 with Spring driving telescoping valve 402.
Fig. 4 C and 4D sets forth the feature consistent with embodiments of the invention, in this embodiment, not mating between the tip of the sealing the margin of Interference angle or telescoping valve 402 and the tip of valve seat 404 is the deflection based on the maximum telescoping valve calculated, and this deflection is because gas pressure bends telescoping valve 402 between piston top ring 414 and valve seat 404.Interference angle can be adjusted to make in maximum deflection place as shown in Fig. 4 C and 4D series, and the inward flange (being namely exposed to the edge of high combustion chamber pressures) at the cone seal edge of telescoping valve 402 keeps in touch with valve seat all the time.Interference angle advantageously can be not more than Maximum Contact area between the necessary sealing the margin guaranteeing telescoping valve 402 and valve seat 404 to provide maximum cooling.Once Interference angle is defined, the size of spring can be made into guarantee that the air pressure on the marginal gap of sealing the margin can not cause telescoping valve 402 lifting to lift off a seat 404.The hole size of block and the position of cylinder-bore can advantageously be defined as telescoping valve 402 can be arranged on valve seat 404, thus make valve central axis in the plane of valve seat 404 and without the need to contact block sidewall.The Interference angle being greater than about 1 degree can be conducive to thin flexible valve.Interference angle can be used to harder valve at about 0 degree in the scope of 1 degree.Favourable valve thickness and material can be determined based on the relation between surge pressure, cylinder bore and required maintenance seal force.
Fig. 4 E illustrates the potential impact using phase shift piston movement to provide the variable compression ratio in opposed piston type engine.Can early than reaching the top dead center position in firing chamber 126 at back piston 412b and moving back to bottom dead center before ignition at first piston 412a, this movement can be timed and occur in close to reaching its top dead center position at back piston.Therefore, the height burning that the first telescoping valve 402a can be allowed to expose more than allowing the second telescoping valve 402b to be exposed to firing chamber 126 at back piston 412b at first piston 412a is pressed.In this case, the Interference angle of the first telescoping valve 402a can be advantageously comparatively large, and it is subject to bending greatly because the larger surface area of the first valve experienced by the peak combustion pressure in firing chamber 126.
Similar effect can appear in variable compressive opposed piston type engine, in this motor, variable compression ratio is provided by connection opposed pistons and arbor, and this arbor can be transferred to the location of the top dead center position changing piston along its reciprocating relevant piston shaft.In this example, shown in Fig. 4 E, occur in the top dead center of two pistons, at the maximum current compression position of motor.When engine operation is that effect is the most remarkable in the configuration of comparatively low compression ratio, as the arbor rotated, and the top dead center position of secondary piston therefore, by by the center rotating as much as possible from motor.
Fig. 4 F shows the sealing the margin of the telescoping valve 402 with multiple angle.The sharp edge that sealing the margin originally could " be repaiied and cut " to angle 422 effectively heats to eliminate partial sleeves valve 402 too fast.Second, next angle 424 can be matched the angle of valve seat can advantageously have the Interference angle comprised.3rd angle 426 can be supplementary angle, and it is more precipitous than telescoping valve 402 wrapping angle, so when telescoping valve 402 and valve seat 404 wear and tear, telescoping valve 402 never bends to valve 402, and to touch valve seat 404 in relief areas such.In such system wear, telescoping valve 402 is about pivot flexure, and this pivot can not shift out to allow excessive pressure to be formed on valve top, valve top place it can acting in opposition in keep telescoping valve 402 close spring force.
In other embodiments, Interference angle can change with the angle of valve seat.If select 30 degree of shallow angles to open raising flow coefficient by valve, in some cases, the friction between valve and valve seat is not high enough to maintain valve from expanding into inclination due to gas load.This deficiency may cause the difference of the accumulated angle between valve and valve seat.In the ordinary course of things, such bending can guarantee that inward flange keeps in touch.
Because valve expands under stress, so the strength of shallow angle and deficiency or friction can make valve slip over valve seat surface.In a kind of mode, this effect can improve the wear rate of assembly.But in a further mode of operation, scraping action can help the formation reducing deposit also can strengthen the ability in the working life of sealed valve in some cases practically.
In another embodiment, the reflex angle seal side of telescoping valve can be provided.Adopt the rotary solids at conical section or some other tip can contribute to location and the sealing of valve in the end of telescoping valve.But the end surface being exposed to the valve of combustion gas can tend to positive opening valve.The geometrical shape of change valve end part seal, as described below, the power kept needed for closedown can be reduced.
Fig. 5 A illustrates the sectional view of the valve tip geometry of two telescoping valves 402a, 402b in opposed piston type engine 500, and opposed piston type engine 500 has the taper shape of 45 degree or the rotary seal face solid with valve seat 404 at other tips.Similar valve end or the edge geometry of sealing also can be used in the motor except opposed piston type engine.The definition cone of the first and second sealing surfaces of two telescoping valves 402 or the axle of the solid at other tips are equivalent to the axle of the central shaft of valve 502 and the motion of piston.The summit of the rotary solids at each circular cone or other tips is by the closed position towards respective valve, or in other words by the center (such as, towards the position of immediate piston near top dead center) towards motor its base surface to respective arbor.Shown in the solid of rotating part at circular cone or other tips can effectively for sealing (can with the conical seal (contact) face angle except 45 degree).But the part on the flat sealing the margin surface 504 of each telescoping valve 402 is exposed to the burning air pressure in firing chamber 126, it tends to drive each valve to open.By adding slight interference between the two, causing surface to meet the inner region of sealing surfaces, the area of exposure can and be minimized, but expose that valve face is long-pending can not be reduced to zero and not introduce impracticable sharp edge.
But, in motor 500 as shown in Figure 5 B, the marginal gap of the needs in combustion zone can be reduced with the reverse solid of the taper of each telescoping valve 402 or the rotation geometry shape at other tips of little Interference angle, because inner side wedge angle can be tilt, such as 135 degree instead of 45 degree.In this example, the summit of circular cone or rotary conic solid is oriented to the open position of each telescoping valve, or in other words towards the respective arbor of each piston.Along with Interference angle biasing contact is towards the application of the internal edge of valve sealing surface, the valve top area 504 being exposed to gas just can minimize widely.Sealing surface can reduce to 45 degree of marginal gaps on the shape valve of top, the side of being mostly in certain embodiments, and its port that can reduce from valve base sealing lip disturbs.The unnecessary area being exposed to combustion gas can be a part for valve seat, and therefore can cause not having resulting net force to be applied on valve.Fig. 5 C and 5D shows extra engine configurations 500, and it comprises the illustrated examples of the alternative arrangements consistent with this embodiment.
Valve seat as described in Figure 5 configures " cascade " seat surface caused also may destroy port flow.Use springy or flexible flowing smoother 602 as shown in the example system 600 in Fig. 6 A, Fig. 6 B, Fig. 6 C and Fig. 6 D for correcting a kind of possible configuration of entrance stream.As shown in Figure 6A, when telescoping valve 402a closes, the retracted position that flow smoother 602 can push, and when telescoping valve 402a opens, flow smoother 602 rebounds with smooth entry flow.Port 604,606 can be designed such that the natural streamline of port flows reposefully with angle of valve seat, in " negative angle approach ", particularly so-called cylinder port (such as CO-PENDING and the international patent application no PCT/US2010/046095 that owns together described in), its middle port approach is mainly from direction as shown in Figure 6A.
The fluid flowing passage of the port orientations of the configuration shown in Fig. 6 A generally guides the Main way of fluid to flow away from engine center 608, likely produces the flow coefficient be not expected in some cases.Along with port keeps " positive angle " approach, the main streamline of its middle port points to engine center, and the size of valve reservoir can be made into be convenient to form lower resistance recirculation reservoir 610 without the need to upsetting overall flow in valve seat 404.The example of positive-angle approach port is shown in Fig. 6 A and Fig. 6 B.Fig. 6 D shows inlet stream, the configuration of recirculation suppression relief opening of the spring-biased consistent with the embodiment of the present invention.The outward edge of telescoping valve has contrary sharp edge gap, complete edge to that indicated in the drawings alternatively.Thisly softening be relevant to telescoping valve distortion under gas pressure and can have an extra benefit.This valve may spread to a certain degree under circumference stress, but valve spring still can by its pushed home.But if valve spring force is inadequate, the taper on the outside of Sealing may be used for wedge and is pressed on another angle character 612 of valve seat to resist circumference stress.Such as, the solid at other tip of the second conical or angle of swing surperficial 612 can be formed on valve seat, and is biased go back to the inside to firing chamber 126 with other the solid at tip of conical or angle of swing.The solid at other tips of the salable contrary taper in inside edge of telescoping valve 402b or the rotation geometry shape of valve seat 404, but the solid that outward edge is biased to other tips on the second conical ground or angle of swing surface can help the bending of the sealing the margin resisting telescoping valve 402b further." wedging " action of correction in certain embodiments can realize being formed by press-in spring element 614 the slightly soft opposing had to allow gas seal compared with low-risk.Spring insert 614 part that can be added as valve seat 404 props up the solid at the taper of valve seat or other tips of rotating part with the sealing the margin of biased telescoping valve 402a.
An alternative embodiment of the invention provides the various functions about double-walled gas auxiliary socket valve.As mentioned above, the key components of valve seal in reciprocating telescoping valve motor.Leakage of oil through Sealing can change burning capacity attribute and directly contribute to discharge.The temperature reducing the sleeve surface contacted with Sealing is useful.Therefore, consistent with some embodiments, " umbrella " valve can be used, and the valve end in umbrella valve has double-walled and the surface that valve oil Sealing props up is directly cooling.
It also can be useful for attempting to push valve open by minimizing gas load, because this can cause realizing better sealing with lower valve spring force.The design of lip valve can be used, and wherein cylinder pressure can be used for the contact force improving valve, instead of weakens it.The problem of umbrella cover cylinder is the complexity manufactured, and how suitably the problem of lip valve is break-in cylinder and valve lip.Double-walled valve concept discussed in this article can by being in harmonious proportion this two problems with the combination valve of two or three assemblies of slice weldering assembling.
The example of valve as shown in Figure 7 A, its not necessarily pro rata or with suitable Aspect Ratio display.Valve 700 can comprise the outer body 704 of inside subject 702.Inside subject 702 as casing surface, thus can provide the to-and-fro motion of a surface run for the piston in telescoping valve.Outer body 704 can as sealing surface, and can be formed gas pressure sealing lip 706, cooling chamber 710 outer wall and sealing operation area 712, the outer wall of cooling chamber 710 is formed between inside subject 702 and outer body 704, and sealing operation area 712 and the seal ring between valve and engine main body carry out alternately.
Inside subject 702 comprise tubular portion as shown in Figure 7 B alternatively and can be formed and pressure releases to make it can through heat cycles and without residual deformation.The assembly forming inside subject 702 shearing length, shaping and eliminate necessary pressure to close to final form alternatively, and break-in on surface 714 within it.Operation for the formation of inside subject 702 can comprise polishing and forming operation.
Outer body 704 can also comprise pipe portion as seen in figure 7 c.Outer tube body part can form operation and generates angled lip 716 with at one end upper and form square cut length on an opposite end.Entrance and exit 720 for cooling fluid can be added by punching press, impression or cutting process.Cylinder outer surface 722 can ground connection to provide good operation surface, the internal surface 724 of outer body 704 is owing to lacking and the interaction on other surfaces and not needing well by break-in.Equally, block can be advantageously heat-staple and have good operation shape.
The example of the telescoping valve that the double-walled gas of the assembling in motor 800 is assisted is shown in Fig. 8.Inside subject 702 and outer body can be assembled by bottom retaining ring 802 and be placed in stove brazing process.Thermal distortion under slice weldering can be advantageously little of as much as possible the form keeping soldering good.Other candidates connecting two main bodys can include but not limited to, electron beam or inertia production weld, scolding tin, and may be even high performance tackiness agents.Fig. 8 also illustrates the extra details about angled antelabium 716, and it can be inwardly outstanding to provide a surface through the internal surface of inside subject 702, and this surface receives to assist to promote the high chamber pressure that valve props up the mode orientation of valve seat 404.
When opposed piston type engine by typically with cylinder axis (the reciprocating axle of piston) parallel installation time, a kind of possible configuration of valve cooling supply is positioned on the top of telescoping valve by oil spurts mouth 902, and draining reservoir 904 is positioned the bottom shown in valve body 900 in Fig. 9 A.Oil can inject the coolant jacket be formed between inner valve body 702 as above and outside valve body 704, splashes around and is discharged.Periphery around valve places some cooling fluid relief openings and one or more spout is necessary, to keep the flowing consistent with cooling fluid.A kind of method of the multiple cooling fluid relief openings in outer valve sleeve is provided to be in outer body 704 as shown in Figure 9 B, form longitudinally " gill portion " 906.The discharge surface that these features can provide, and the rigidity simultaneously increasing outer main body 704.The another kind of method of sclerosis cooling port is placing circular pit 910 around oval port 912, wherein can be described to " opal " port of example as shown in Figure 9 C.Two rows alternately port 914 can be located to improve around outer body 704 periphery as shown in fig. 9d cooling filling.If alternately the port area of port 914 is overlapping, then no matter be open at valve or in closing process, can be used at any some port of valve stroke.
Also may construct the pattern of the valve only having two assemblies, its prerequisite holds enough tight permissible error.If inside subject valve lower lip was formed, prunes, heats elimination before break-in operation, enough permissible errors can be kept.The flange of the outside formation of inside subject also can extend past outer body, and valve rocker arm may act on flange.This rocking arm can act on valve 1000 as shown in Figure 10 by engagement a pair groove 1002, and this is visible in Fig. 10 in groove.This scheme can provide the advantage of check valve rotary valve a little, so cooling nozzle always can be directed to valve.Figure 10 also illustrates that another organizes the cooling filling/weep hole 1004 bottom inside subject be optionally included.
In one or more embodiments, two assembly sleeve does not need air clearance/cooling gap.If inside subject is sufficiently stiffer than outer body, then it before outer body is crushed on it with regard to ground connection and break-in.Outer body lip provides gas supplemental characteristic, and based on this feature, the pressure effect of firing chamber impels telescoping valve to prop up valve seat further, and inside subject provides hoop intensity and shape.Cooperation between two main bodys can be resisted and be attempted to promote the gas that inside subject leaves outer body.Connected member between inside and outside can be formed to reduce Separating force and gap volume as far as possible.The pressing that opposing is separated can be applied to the valve with the air/cooling gap shown in Fig. 7 to Figure 10, also can be used for the valve not having such gap.
In another embodiment, piston type ring can be used for seal sleeve valve.As mentioned above, the key component of valve seal in reciprocating telescoping valve motor.Oil leakage through Sealing can change burning capacity attribute and directly contribute to discharge.In addition, Sealing generally heat, work under rugged environment, the part contact the hottest with telescoping valve.Therefore, the performance of Sealing is crucial, is exposed to the use that heat can prevent polymer lip seal.
Traditional piston ring has the advantage of higher thermal conductivity and higher temperature tolerance usually than polymer lip seal.By their conduction, they are by also reducing peak value telescoping valve temperature at the some conduction energy not being conducted through polymeric seal valve away from valve.But tip gap is problematic in valve seal application, because oil may directly permeate.
The embodiment of the present invention can comprise one group of seal element assembling to form spendable Sealing 1100 as illustrated in figure 11 a.Sandwich structure can be created, and top layer 1102 is shells of the high temperature polymer in oblateness, the external diameter being just greater than telescoping valve of its internal diameter.Mesosphere can comprise the index piston ring 1,104 a pair with parallel end face and bottom surface and index feature 1106 does not line up to make tip gap.Preferably, index feature 1106 can be symmetrical to make single part can be used for two or a pair of ring 1104.Bottom 1110 can comprise wavy spring, is similar to the separator spring that the promotion in traditional oil ring is superimposed.
The sealing of antagonism valve is implemented primarily of lower scraping ring as shown in Figure 11 B.Tip gap in the lower ring 1104b of pair of pistons ring can be covered by the upper sealing ring 1104a of a centering.Upper sealing ring 1104a can push polymer seal 1102, and it can keep sealing between main body 1112 at upper sealing ring 1104a and sealing storehouse.Polymer seal 1102 can also have one around the skirt section 1114 of its periphery to seal the external diameter of upper sealing ring 1104a.This skirt section feature also can be implemented by independent flexible polymer block.Skirt section 1114 also can have increases ring to the function of valve surface tension force.
The external diameter of the valve that this method may need, by break-in, enough can run seal ring to make Oil keeping and can not excessive wear.In addition, can be necessary with the Sealing operated from the contrary mode of piston ring.Piston ring can be compressed also seal on the outer surface to extrapolation.Valve packing ring can be stretched to and inwardly pulls and seal on inner surface.The manufacture method of such ring can be different from standard ring.Another kind method is the similar coil being greater than a circle scraping cross section 1120 as shown in fig. 11c.The complete surface of the valve that this configuration can be wiped off effectively, avoids tip gap problem, but may need circumference polymer seal, because it does not exist the tabular surface being convenient to seal.
Figure 12 shows flow chart 1200, and it sets forth the method characteristic consistent with one or more embodiment of the present invention.In 1202, telescoping valve is mobile to control to flow through engine port between open and closed positions by valve actuating structure.Telescoping valve comprises valve body, valve body at least in part around at least one with the piston of reciprocating manner movement.Telescoping valve and at least one piston described define the firing chamber of internal-combustion engine at least in part.In 1204, when telescoping valve is moved to closed position, the sealing the margin of telescoping valve is pushed by the Driving force produced by valve actuating structure and props up valve seat.Valve supplemental characteristic contributes to valve brake structure and resists the power contrary with the Driving force in 1206 produced by internal-combustion engine.At least one in telescoping valve and valve seat comprises valve supplemental characteristic.The power contrary with Driving force produced by internal-combustion engine can be included in the pressure of the combustion gas in firing chamber, and this pressure acts on the exposed surface of sealing the margin on the direction contrary with the valve closing force of valve brake structure.
Embodiment in above-mentioned explanation does not represent the consistent embodiment of invention all and described here.On the contrary, they are only some some examples consistent with described invention related fields.Although some changes are described in detail at this, other amendment or supplement are also possible.Especially, further feature and/or change can be provided in except described example.Such as, above-described embodiment can be applied to the various combination of disclosed feature and/or combination and the sub-portfolio of sub-portfolio and above-mentioned discloseder further features.In addition, described here and logic flow that is that be described in the drawings does not necessarily require shown particular order or continuous order to obtain results needed.Claims can comprise other concrete example or embodiment.

Claims (36)

1. the system for using in internal-combustion engine, comprising:
Telescoping valve, comprise at least in part around at least one with the valve body of the piston of reciprocating manner movement, described telescoping valve and at least one piston described define the firing chamber of described internal-combustion engine at least in part;
Valve brake structure, moves described telescoping valve between open and closed positions to control to flow through the port of described internal-combustion engine; And
Valve seat, when described telescoping valve is moved to institute's limit closed position, the sealing the margin of described telescoping valve is promoted to prop up and described valve seat by described valve brake structure, at least one of described telescoping valve and described valve seat comprises valve supplemental characteristic, described valve supplemental characteristic helps described valve brake structure to resist the power contrary with described Driving force produced by described internal-combustion engine, the described power contrary with described Driving force that is that produced by described internal-combustion engine is included in the pressure of combustion gas in described firing chamber, described pressure acts on the exposed surface of described sealing the margin on the direction contrary with the valve closing force of described valve brake structure, described valve supplemental characteristic comprises the Interference angle be formed between the first sealing surfaces on the described sealing the margin of described valve and the second sealing surfaces on described valve seat, when described Interference angle is configured to the radial directed power when described telescoping valve causes due to the combustion-gas pressure in described firing chamber and is bent outwardly, the area of described exposed surface is reduced by the formation reducing the clearance opening between described sealing the margin and described valve seat, described Interference angle comprises the difference between the first cone angle of described sealing the margin and the second cone angle of described valve seat, described first cone angle and described second cone angle do not mate, described Interference angle is formed between the first sealing surfaces on described sealing the margin and the second sealing surfaces on described valve seat, described first sealing surfaces is made into the first portion that shape is the first most advanced and sophisticated solid rotated, described first portion has the first summit towards described first sealing surfaces taper, described second sealing surfaces is made into the second portion that shape is the second most advanced and sophisticated solid rotated, described second portion has the second summit towards described second sealing surfaces taper, the central shaft of each and described firing chamber of the first most advanced and sophisticated solid of described rotation and the second most advanced and sophisticated solid of described rotation shares its running shaft.
2. the system as claimed in claim 1, the second most advanced and sophisticated solid that the first most advanced and sophisticated solid of wherein said rotation comprises the first circular cone and described rotation comprises the second circular cone.
3. the system as described in claim arbitrary in claim 1 to 2, wherein said first summit and described second summit are all towards described closed position.
4. the system as described in claim arbitrary in claim 1 to 2, wherein said first summit and described second summit are all towards described open position.
5. system as described in claim 1, wherein said Interference angle comprises the inclination Interference angle between described sealing the margin and described valve seat.
6. the system as described in claim 1 or 5, wherein said valve brake structure comprises spring, and the size of described spring is made into guarantee that maximum gas pressure can not promote described sealing the margin and depart from described valve seat.
7. the system for using in internal-combustion engine, comprising:
Telescoping valve, comprise at least in part around at least one with the valve body of the piston of reciprocating manner movement, described telescoping valve and at least one piston described define the firing chamber of described internal-combustion engine at least in part;
Valve brake structure, moves described telescoping valve between open and closed positions to control to flow through the port of described internal-combustion engine; And
Valve seat, when described telescoping valve is moved to described closed position, the sealing the margin of described telescoping valve is promoted by described valve brake structure and props up described valve seat, at least one of described telescoping valve and described valve seat comprises valve supplemental characteristic, described supplemental characteristic helps described valve brake structure to resist the power contrary with described Driving force produced by described internal-combustion engine, the described power contrary with described Driving force that is that produced by described internal-combustion engine is included in the pressure of the combustion gas in described firing chamber, described pressure acts on the exposed surface of described sealing the margin on the direction contrary with the valve closing force of described valve brake structure, described valve supplemental characteristic comprises the Interference angle be formed between the described sealing the margin of described valve and described valve seat, reach Interference angle when being configured to the radial directed power when described telescoping valve causes due to the combustion-gas pressure in described firing chamber and being bent outwardly, the area of described exposed surface is reduced by the formation reducing the clearance opening between described sealing the margin and described valve seat, described Interference angle comprises the difference between the first cone angle of described sealing the margin and the second cone angle of described valve seat, described first cone angle and described second cone angle do not mate, described Interference angle is based on the maximum deflection of described telescoping valve estimated by the pressure maximum of the described combustion gas in described firing chamber, even if described Interference angle makes the inward flange of described sealing the margin also keep the contact with described valve seat in maximum deflection place.
8. system as claimed in claim 7, wherein said Interference angle comprises the inclination Interference angle between described sealing the margin and described valve seat.
9. system as claimed in claim 7 or 8, wherein said valve brake structure comprises spring, and the size of described spring is made into guarantee that maximum gas pressure can not promote described sealing the margin and depart from described valve seat.
10. the system for using in opposed piston internal combustion engine, comprising:
Comprise the telescoping valve of a valve body and comprise the second telescoping valve of the second valve body, described sleeve valve body is centered around back piston at least in part around at first piston and described second sleeve valve body at least in part, described first piston and described at back piston with the to-and-fro motion between respective top dead center and bottom dead center position of inharmonic mode, thus make described at first piston prior to described its top dead center position that arrived before back piston arrives its top dead center position to provide variable compression ratio performance, described telescoping valve, described second telescoping valve, described in first piston and the described firing chamber defining described opposed piston internal combustion engine at back piston at least in part,
Valve brake structure, between the respective open position and closed position of described telescoping valve and described second telescoping valve, mobile described telescoping valve and described second telescoping valve are to control at least two ports flowing through described opposed piston internal combustion engine;
Valve seat, when described telescoping valve is moved to described closed position, the sealing the margin of described telescoping valve is promoted to prop up described valve seat by described valve brake structure, at least one of described telescoping valve and described valve seat comprises valve supplemental characteristic, described valve supplemental characteristic helps described valve brake structure to resist the power contrary with described Driving force produced by described internal-combustion engine, the described power contrary with described Driving force that is that produced by described internal-combustion engine is included in the pressure of the combustion gas in described firing chamber, described pressure acts on the exposed surface of described sealing the margin on the direction contrary with the valve closing force of described valve brake structure, described valve supplemental characteristic is included in the Interference angle between the described sealing the margin of described valve and described valve seat, when described Interference angle is configured to the radial directed power when described telescoping valve causes due to the combustion-gas pressure in described firing chamber and is bent outwardly, the area of described exposed surface is reduced by the formation reducing the clearance opening between described sealing the margin and described valve seat, described Interference angle comprises the difference of the valve of the first cone angle of described sealing the margin and the second cone angle of described valve seat, described first cone angle and described second cone angle do not mate, and
Second valve seat, the second sealing the margin of described second telescoping valve is promoted to prop up described second valve seat, the second Interference angle being less than described Interference angle between described second sealing the margin and described second valve seat of described second telescoping valve by described valve brake structure.
11. systems as claimed in claim 10, wherein said Interference angle comprises the inclination Interference angle between described sealing the margin and described valve seat.
12. systems as described in claim 10 or 11, wherein said valve brake structure comprises spring, and the size of described spring is made into guarantee that maximum gas pressure can not promote described sealing the margin and depart from described valve seat.
13. 1 kinds, for the system used in opposed piston internal combustion engine, comprising:
Comprise the telescoping valve of a valve body and comprise the second telescoping valve of the second valve body, described sleeve valve body at least in part around main piston and described second sleeve valve body at least in part around secondary piston, move back and forth between respective top dead center on the first and second respective arbors of described main piston and described piston and lower dead center, described second arbor can rotate along the travel axis of described piston, thus make, compared with described piston in low compression ratio configuration, there is top dead center position, described top dead center position is distal to the distance apart from described main piston apart from the distance at described opposed piston internal combustion engine center, described telescoping valve, described second telescoping valve, described main piston and described piston define the firing chamber of described opposed piston internal combustion engine at least in part,
Valve brake structure, between the respective open position and closed position of described telescoping valve and described second telescoping valve, mobile described telescoping valve and described second telescoping valve are to control at least two ports flowing through described opposed piston internal combustion engine;
Valve seat, when described telescoping valve is moved to described first closed position, the sealing the margin of described telescoping valve is promoted by described valve brake structure and props up described valve seat, at least one of described telescoping valve and described valve seat comprises valve supplemental characteristic, described valve supplemental characteristic helps described valve brake structure to resist the power contrary with described Driving force produced by described internal-combustion engine, the described power contrary with described Driving force that is that produced by described internal-combustion engine is included in the pressure of the combustion gas in described firing chamber, described pressure acts on the exposed surface of described sealing the margin on the direction contrary with the valve closing force of described valve brake structure, described valve supplemental characteristic is included in the Interference angle between the described sealing the margin of described valve and described valve seat, when described Interference angle is configured to the radial directed power when described telescoping valve causes due to the combustion-gas pressure in described firing chamber and is bent outwardly, the area of described exposed surface is reduced by the formation reducing the clearance opening between described sealing the margin and described valve seat, described Interference angle comprises the difference between the first cone angle of described sealing the margin and the second cone angle of described valve seat, described first cone angle and described second cone angle do not mate,
Second valve seat, the second sealing the margin of described second telescoping valve is promoted to prop up described second valve seat, the second Interference angle being greater than described Interference angle between described second sealing the margin and described second valve seat of described second telescoping valve by described valve brake structure.
14. systems as claimed in claim 13, wherein said Interference angle comprises the inclination Interference angle between described sealing the margin and described valve seat.
15. systems as described in claim 13 or 14, wherein said valve brake structure comprises spring, and the size of described spring is made into guarantee that maximum gas pressure can not promote described sealing the margin and depart from described valve seat.
16. 1 kinds, for the system used in internal-combustion engine, comprise
Telescoping valve, comprise at least in part around at least one with the valve body of the piston of reciprocating manner movement, described telescoping valve and at least one piston described define the firing chamber of described internal-combustion engine at least in part; And
Valve brake structure, moves described telescoping valve between open and closed positions to control to flow through the port of described internal-combustion engine; And
Valve seat, when described telescoping valve is moved into described closed position, the sealing the margin of described telescoping valve is promoted by described valve brake structure and props up described valve seat, at least one of described telescoping valve and described valve seat comprises valve supplemental characteristic, described valve supplemental characteristic helps described valve brake structure to resist the power contrary with described Driving force produced by described internal-combustion engine, the described power contrary with described Driving force that is that produced by described internal-combustion engine is included in the pressure of the combustion gas in described firing chamber, described pressure acts on the exposed surface of described sealing the margin on the direction contrary with the valve closing force of described valve brake structure, described valve supplemental characteristic is included in the Interference angle between the described sealing the margin of described valve and described valve seat, when described Interference angle is configured to the radial directed power when described telescoping valve causes due to the combustion-gas pressure in described firing chamber and is bent outwardly, the area of described exposed surface is reduced by the formation reducing the clearance opening between described sealing the margin and described valve seat, described Interference angle comprises the difference between the first cone angle of described sealing the margin and the second cone angle of described valve seat, described first cone angle and described second cone angle do not mate, described sealing the margin comprises multiple angle, described multiple angle comprises first jiao, described first jiao of other sharp edge softening or cut out described sealing the margin are to eliminate heating too fast of sealing the margin, be matched to second jiao of described angle of valve seat and comprise described Interference angle, and substantially the more precipitous than the wrapping angle of described telescoping valve and described valve seat the 3rd, relax angle to make when described telescoping valve and the described prooving of valve seat, described telescoping valve can not bend too many to such an extent as to described sealing the margin and described valve seat and the 3rd, relief areas contacts.
17. systems as claimed in claim 16, wherein said Interference angle comprises the inclination Interference angle between described sealing the margin and described valve seat.
18. systems as described in claim 16 or 17, wherein said valve brake structure comprises spring, and the size of described spring is made into guarantee that maximum gas pressure can not promote described sealing the margin and depart from described valve seat.
19. 1 kinds of methods for operating internal-combustion engines, the method comprises:
Moving sleeve valve is to control the port flowing through described internal-combustion engine between open and closed positions, described telescoping valve comprises valve body, described valve body at least in part around at least one with the piston of reciprocating manner movement, described telescoping valve and at least one piston described define the firing chamber of described internal-combustion engine at least in part, and described movement is implemented by valve brake structure;
When described telescoping valve is moved to closed position, the sealing the margin that the Driving force produced by described valve actuating structure promotes described telescoping valve props up valve seat;
Described valve brake structure is helped to resist the power contrary with described Driving force produced by described internal-combustion engine by valve supplemental characteristic, at least one of described telescoping valve and described valve seat comprises described valve supplemental characteristic, the described power contrary with described Driving force that is that produced by described internal-combustion engine is included in the pressure of the combustion gas in described firing chamber, described pressure acts on the exposed surface of described sealing the margin on the direction contrary with the valve closing force of described valve brake structure, described valve supplemental characteristic is included in the Interference angle between the described sealing the margin of described valve and described valve seat, when described Interference angle is configured to the radial directed power when described telescoping valve causes due to the combustion-gas pressure in described firing chamber and is bent outwardly, the area of described exposed surface is reduced by the formation reducing the clearance opening between described sealing the margin and described valve seat, described Interference angle comprises the difference of the valve of the first cone angle of described sealing the margin and the second cone angle of described valve seat, described first cone angle and described second cone angle do not mate, described Interference angle is formed between the first sealing surfaces on described sealing the margin and the second sealing surfaces on described valve seat, described first sealing surfaces is made into the first portion that shape is the first most advanced and sophisticated solid rotated, described first portion has the first summit towards described first sealing surfaces blank, described second sealing surfaces is made into the second portion that shape is the second most advanced and sophisticated solid rotated, described second portion has the second summit towards described second sealing surfaces taper, the central shaft of each and described firing chamber of the first most advanced and sophisticated solid of described rotation and the second most advanced and sophisticated solid of described rotation shares its running shaft.
20. methods as claimed in claim 19, the second most advanced and sophisticated solid that the first most advanced and sophisticated solid of wherein said rotation comprises the first circular cone and described rotation comprises the second circular cone.
21. methods as described in the arbitrary claim in claim 19 to 20, wherein said first summit and described second summit are all towards described closed position.
22. methods as described in the arbitrary claim in claim 19 to 20, wherein said first summit and described second summit are all towards described open position.
23. methods as claimed in claim 19, are included in the inclination Interference angle between described sealing the margin and described valve seat comprising described Interference angle.
24. methods as described in claim 19 or 20, wherein said valve brake structure comprises spring, and the size of described spring is made into guarantee that maximum gas pressure can not promote described sealing the margin and depart from described valve seat.
25. 1 kinds of methods for operating internal-combustion engines, the method comprises:
Moving sleeve valve is to control the port flowing through described internal-combustion engine between open and closed positions, described telescoping valve comprises valve body, described valve body at least in part around at least one with the piston of reciprocating manner movement, described telescoping valve and at least one piston described define the firing chamber of described internal-combustion engine at least in part, and described movement is implemented by valve brake structure;
When described telescoping valve is moved to closed position, the sealing the margin promoting described telescoping valve by described valve actuating structure props up valve seat; And
Described valve brake structure is helped to resist the power contrary with described Driving force produced by described internal-combustion engine by valve supplemental characteristic, at least one of described telescoping valve and described valve seat comprises described valve supplemental characteristic, the described power contrary with described Driving force that is that produced by described internal-combustion engine is included in the pressure of the combustion gas in described firing chamber, described pressure acts on the exposed surface of described sealing the margin on the direction contrary with the valve closing force of described valve brake structure, described valve supplemental characteristic comprises the Interference angle between the described sealing the margin of described valve and described valve seat, when described Interference angle is configured to the radial directed power when described telescoping valve causes due to the combustion-gas pressure in described firing chamber and is bent outwardly, by reducing the formation of the clearance opening between described sealing the margin and described valve seat to reduce the area of described exposed surface, described Interference angle is based on the maximum deflection of described telescoping valve estimated by the pressure maximum of the described combustion gas in described firing chamber, even if described Interference angle make the inward flange of described sealing the margin maximum deflection place also keep with described valve seat connect angle worm.
26. methods as claimed in claim 25, are included in the inclination Interference angle between described sealing the margin and described valve seat comprising described Interference angle.
27. methods as described in claim 25 or 26, wherein said valve brake structure comprises spring, and the size of described spring is made into guarantee that maximum gas pressure can not promote described sealing the margin and depart from described valve seat.
28. 1 kinds for operating the method for opposed piston internal combustion engine, the method comprises:
Mobile described telescoping valve and described second telescoping valve between the respective open position and closed position of telescoping valve and the second telescoping valve, to control at least two ports flowing through described opposed piston internal combustion engine, described telescoping valve comprises at least in part around the valve body at first piston, and described second telescoping valve comprises the second valve body being centered around back piston at least in part, described first piston and described at back piston with the to-and-fro motion between respective top dead center and bottom dead center position of inharmonic mode, thus make described at first piston prior to described its top dead center position that arrived before back piston arrives its top dead center position to provide variable compression ratio performance, described telescoping valve, described second telescoping valve, described in first piston and the described firing chamber defining opposed piston internal combustion engine at back piston at least in part,
When described telescoping valve is moved to closed position, the sealing the margin promoting described telescoping valve by described valve actuating structure props up valve seat;
Described valve brake structure is helped to resist the power contrary with described Driving force produced by described internal-combustion engine by valve supplemental characteristic, at least one of described telescoping valve and described valve seat comprises described valve supplemental characteristic, the described power contrary with described Driving force that is that produced by described internal-combustion engine is included in the pressure of the combustion gas in described firing chamber, described pressure acts on the exposed surface of described sealing the margin on the direction contrary with the valve closing force of described valve brake structure, described sealing the margin between described in described valve supplemental characteristic is included in and the Interference angle between described valve seat, when described Interference angle is configured to the radial directed power when described telescoping valve causes due to the combustion-gas pressure in described firing chamber and is bent outwardly, by reducing the formation of the clearance opening between described sealing the margin and described valve seat to reduce the area of described exposed surface, described Interference angle comprises the difference between the first cone angle of described sealing the margin and the second cone angle of described valve seat, described first cone angle and described second cone angle do not mate, and when described second telescoping valve is moved to closed position, the second sealing the margin being promoted described second telescoping valve by described valve actuating structure props up the second valve seat, the second Interference angle being less than described Interference angle between described second sealing the margin and described second valve seat of described second telescoping valve.
29. methods as claimed in claim 28, are included in the inclination Interference angle between described sealing the margin and described valve seat comprising described Interference angle.
30. methods as described in claim 28 or 29, wherein said valve brake structure comprises spring, and the size of described spring is made into guarantee that maximum gas pressure can not promote described sealing the margin and depart from described valve seat.
31. 1 kinds for operating the method for opposed piston internal combustion engine, the method comprises:
Mobile described telescoping valve and described second telescoping valve between the respective open position and closed position of telescoping valve and the second telescoping valve, to control at least two ports flowing through described opposed piston internal combustion engine, described telescoping valve comprises and comprises at least in part around the second valve body of secondary piston around the valve body of main piston and described second telescoping valve at least in part, move back and forth between respective top dead center on the first and second respective arbors of described main piston and described piston and lower dead center, described second arbor can rotate along described piston driving shaft, thus make, compared with described piston in low compression ratio configuration, there is top dead center position, described top dead center position is distal to the distance apart from described main piston apart from the distance at described opposed piston internal combustion engine center, described telescoping valve, described second telescoping valve, described main piston and described piston define the firing chamber of opposed piston internal combustion engine at least in part, described movement is implemented by valve brake structure,
When described telescoping valve is moved to closed position, the sealing the margin promoting described telescoping valve by described valve actuating structure props up valve seat;
Described valve brake structure is helped to resist the power contrary with described Driving force produced by described internal-combustion engine by valve supplemental characteristic, at least one of described telescoping valve and described valve seat comprises described valve supplemental characteristic, the described power contrary with described Driving force that is that produced by described internal-combustion engine is included in the pressure of the combustion gas in described firing chamber, described pressure acts on the exposed surface of described sealing the margin on the direction contrary with the valve closing force of described valve brake structure, described valve supplemental characteristic is included in the Interference angle between the described sealing the margin of described valve and described valve seat, when described Interference angle is configured to the radial directed power when described telescoping valve causes due to the combustion-gas pressure in described firing chamber and is bent outwardly, by reducing the formation of the clearance opening between described sealing the margin and described valve seat to reduce the area of described exposed surface, described Interference angle comprises the difference between the first cone angle of described sealing the margin and the second cone angle of described valve seat, described first cone angle and described second cone angle do not mate, and
When described second telescoping valve is moved to closed position, the second sealing the margin being promoted described second telescoping valve by described valve actuating structure props up the second valve seat, the second Interference angle being greater than described Interference angle between described second sealing the margin and described second valve seat of described second telescoping valve.
32. methods as claimed in claim 31, are included in the inclination Interference angle between described sealing the margin and described valve seat comprising described Interference angle.
33. methods as described in claim 31 or 32, wherein said valve brake structure comprises spring, and the size of described spring is made into guarantee that maximum gas pressure can not promote described sealing the margin and depart from described valve seat.
34. 1 kinds of methods for operating internal-combustion engines, the method comprises:
Moving sleeve valve is to control the port flowing through described internal-combustion engine between open and closed positions, described telescoping valve comprises valve body, described valve body at least in part around at least one with the piston of reciprocating manner movement, described telescoping valve and at least one piston described define the firing chamber of described internal-combustion engine at least in part, and described movement is implemented by valve brake structure;
When described telescoping valve is moved to closed position, the sealing the margin promoting described telescoping valve by described valve actuating structure props up valve seat; And
Described valve brake structure is helped to resist the power contrary with described Driving force produced by described internal-combustion engine by valve supplemental characteristic, at least one of described telescoping valve and described valve seat comprises described valve supplemental characteristic, the described power contrary with described Driving force that is that produced by described internal-combustion engine is included in the pressure of the combustion gas in described firing chamber, described pressure acts on the exposed surface of described sealing the margin on the direction contrary with the valve closing force of described valve brake structure, described valve supplemental characteristic is included in the Interference angle between the described sealing the margin of described valve and described valve seat, when described Interference angle is configured to the radial directed power when described telescoping valve causes due to the combustion-gas pressure in described firing chamber and is bent outwardly, by reducing the formation of the clearance opening between described sealing the margin and described valve seat to reduce the area of described exposed surface, described Interference angle comprises the difference between the first cone angle of described sealing the margin and the second cone angle of described valve seat, described first cone angle and described second cone angle do not mate, described sealing the margin comprises multiple angle, described multiple angle comprises first jiao, described first jiao of other sharp edge softening or cut out described sealing the margin are to eliminate heating too fast of sealing the margin, be matched to second jiao of described angle of valve seat and comprise described Interference angle, and substantially the more precipitous than the wrapping angle of described telescoping valve and described valve seat the 3rd, relax angle to make when described telescoping valve and the described prooving of valve seat, described telescoping valve can not bend too many to such an extent as to described sealing the margin and described valve seat and the 3rd, relief areas contacts.
35., as the method for claim 34, are included in the inclination Interference angle between described sealing the margin and described valve seat comprising described Interference angle.
36. methods as described in claim 34 or 35, wherein said valve brake structure comprises spring, and the size of described spring is made into guarantee that maximum gas pressure can not promote described sealing the margin and depart from described valve seat.
CN201180059309.2A 2010-10-08 2011-10-08 The telescoping valve sealing improved Expired - Fee Related CN103261590B (en)

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